Axle nut

ABSTRACT

An axle nut for preloading a bearing is provided. The axle nut may be used to apply and monitor preload on a bearing or bearing assembly. The axle nut includes a cylindrical body having a first end, a second end having a face adapted to bear against a surface, a longitudinal axis, and an outer surface engagable by a tool; a threaded through-hole directed substantially along the longitudinal axis of the cylindrical body; and at least one recess in the face of the second end of the cylindrical body, the at least one recess adapted to expose at least a portion of the surface the face bears against. The first end of the axle may comprise a nut locking mechanism, for example, the nut locking mechanism may include a counter bore having a plurality of internal projections, such as, gear or spline teeth.

CROSS-REFERENCE TO RELATED APPLICATION

This application is related to pending U.S. patent application Ser. No.11/341,948, filed on Jan. 27, 2006, entitled “Method and Apparatus forPreloading a Bearing”, the disclosure of which is incorporated byreference herein.

This application is a divisional application of U.S. application Ser.No. 11/354,513 filed on Feb. 15, 2006, now U.S. Pat. No. 7,389,579, thedisclosure of which is incorporated by reference herein.

TECHNICAL FIELD

The present invention relates, generally, to methods and apparatus forpreloading antifriction bearings in drive trains, particularly, topreloading and adjusting bearings while monitoring the preload beingapplied.

BACKGROUND OF THE INVENTION

Various means have been devised to simplify the adjustment of axlebearings, specifically, truck axle bearings. It is generally acceptedthat in some bearing installations, for example, axle bearings, the lifeof the bearing will be optimized if the adjustment is made for a slightaxial compressive deflection, for example, about 0.003 inches (wherethis amount is the compressive deflection of the two bearings combined),which is often referred to as “a three thousandths preload.” Typicalprior art methods of creating these preloads are obtained by applyingspecified torques to the bearing assembly, for example, by tighteningthe nut that retains the bearings. However, for several reasons, it istypically extremely difficult to achieve such preload settings underactual in-field conditions, as in a mechanic shop. For example, theassembly of a heavy truck wheel onto a wheel hub assembly is arelatively cumbersome procedure that hinders the mechanic. Moreover, thewheel hub assembly always includes at least one inner seal, usually alip type of seal, which can impose a resistive drag torque component tothe preload torque, particularly when the seal is new.

One of the popular means of adjusting bearing preload by means of anapplied torque is described in the literature provided by the StemcoCompany, of Longview, Tex. (for example, Stemco form 571-2970) andfurther in instructions provided by Stemco (for example, Stemco partnumber 09-571-0006). These instructions are typically packaged withStemco's axle spindle nuts. The accuracy of this and other prior artpreloading methods is limited because they rely on the relationshipbetween assembly torque and axial preload of the bearings, which willvary with variations in torsional resistance or friction of the nutagainst the face of the bearing, and will also vary with variations intorsional resistance or friction of the nut against the spindle thread,the nut against the bearing face, and the aforementioned lip sealpresent in the assembly.

Due to the limitations and disadvantages of these and other prior artbearing preloading methods and devices, there is a need to provideaccurate and repeatable procedures and devices for providing andadjusting bearing preload. Aspects of the present invention overcome thelimitations and disadvantages of the prior art and provide methods andapparatus for creating known, monitorable, uniform preload that is notsubject to the inaccuracies of prior art methods and devices. Moreover,aspects of the present invention are easier to apply by a mechanic.

SUMMARY OF THE INVENTION

The present invention provides improved methods and apparatus forpreloading bearings. In particular, the methods and apparatus of thepresent invention permit the mechanic to monitor the preload during thepreloading procedure to more accurately determine the actual preloadprovided. One aspect of the invention is an apparatus for providing apreload on a bearing, the bearing having an inner race mounted to ashaft and an outer race mounted in a hub, the apparatus including a rodhaving a first end and a second end adapted to be removably mounted tothe shaft; means for compressing the hub against the outer race of thebearing to provide the preload to the bearing, the means for compressingmounted to the rod; and a cylindrical frame positioned between the meansfor compressing the hub and the hub, the cylindrical frame having afirst end adapted to receive a load from the means of compressing thehub and a second end adapted to transmit the load to the hub. In oneaspect, the second end of the cylindrical frame contacts the hub. Inanother aspect, the second end of the cylindrical frame contacts aninner race of a bearing. In another aspect, the apparatus furthercomprises means for monitoring the preload on the bearing

Another aspect of the invention is a method for providing a preload on abearing having an inner race mounted to a shaft and an outer racemounted in a hub, the method including mounting a rod to an end of theshaft; mounting a means for compressing the hub against the outer raceof the bearing to the rod; and actuating the means for compressing thehub to compress the hub against the outer race of the bearing to providethe preload to the bearing. In one aspect, the method further comprisesmonitoring the preload on the bearing.

Another aspect of the invention is an apparatus for providing a preloadto an inboard bearing having an inner race mounted to a shaft and anouter race mounted in a hub and for providing a preload to an outboardbearing having an inner race mounted to the shaft and an outer racemounted in the hub, the outboard bearing spaced from the inboardbearing, the apparatus including an outboard bearing retaining nutadapted to engage a threaded end of the shaft and contact the inner raceof the outboard bearing to retain the preload on the outboard bearing; arod having a first end and a second end adapted to be removably mountedto the shaft; a fluid-containing cylinder mounted to the rod, thecylinder having a cylinder housing mounted to the rod and a pistonadapted to compress the hub against the outer race of the inboardbearing to provide the preload to the inboard bearing; an actuating nutthreaded to the rod and adapted to compress the cylinder housing towardthe piston; and a cylindrical frame positioned between the piston andthe hub having a first end adapted to receive a load from the piston anda second end adapted to transmit the load to the hub and compress thehub against the inner race of the inboard bearing to provide the preloadto the inboard bearing. In one aspect, the apparatus further comprisesmeans for monitoring the pressure of the fluid in the fluid-containingcylinder.

A further aspect of the invention is an apparatus for precisely rotatinga nut, the apparatus including a guide frame comprising a support ringhaving a first side adapted to contact a support and a second sideopposite the first side; and a plurality of posts having first endsmounted to the second side of the support ring and second ends oppositethe first ends; and a tool comprising a set of opposed tines adapted toengage flats on the nut; means for rotating the tines to rotate the nut;and at least two spaced stops adapted to engage at least one of theposts of the guide frame and limit the rotation of the nut to thepredetermined angle defined by the two spaced stops.

A still further aspect of the invention is a method for preciselyrotating a nut, the method including determining a desired preciserotation for the nut; providing a guide frame comprising: a supportplate having a first side adapted to contact a support and a second sideopposite the first side; and a plurality of spaced stops positioned onthe support plate; providing a tool comprising: at least one set ofopposed tines adapted to engage flats on the nut; and a plurality ofspaced stops adapted to engage at least one of the spaced stops of theguide frame, the spaced stops positioned to limit the rotation of thetool to the desired precise rotation for the nut; mounting the tool tothe nut wherein the plurality of tines engage flats on the nut andwherein the at least one stop on the tool engages at least one stop onthe guide frame; and rotating the nut with the tool wherein at least onestop on the tool engages at least one stop on the guide frame whereinthe nut is rotated the desired precise rotation.

A further aspect of the invention is a tool for precisely rotating anut, the tool including: at least one set of opposed tines adapted toengage flats on the nut; means for rotating the plurality of tines torotate the nut; at least one stop adapted to engage at leastcorresponding stop on a fixture mounted adjacent the nut to limit therotation of the nut to a predetermined angle. In one aspect, the atleast one stop on the tool comprises at least one of a post, pin, andrecess.

A further aspect of the invention is an axle nut comprising acylindrical body having a first end, a second end having a face adaptedto bear against a surface, a longitudinal axis, and an outer surfaceengagable by a tool; a threaded through-hole directed substantiallyalong the longitudinal axis of the cylindrical body; and at least onerecess in the face of the second end of the cylindrical body, the atleast one recess adapted to expose at least a portion of the surface theface bears against. In one aspect, the at least one recess comprises atleast one arcuate recess, for example, a plurality of arcuate recessesequally spaced about the perimeter of the face.

Another aspect of the invention is an apparatus for providing a load ona bearing, the bearing having an inner race mounted to a shaft and thebearing retained on the shaft by a nut, the apparatus comprising a rodhaving a first end and a second end adapted to be removably mounted tothe shaft; an adapter comprising a plate having a hole through which therod passes and a plurality of extensions mounted to the plate andadapted to engage the inner race of the bearing with the nut in place;and means for providing a compressive load to the plate of the adapterwhereby the load is provided to the inner race of the bearing with thenut in place. In one aspect, the plurality of extensions is pivotallymounted to the plate. In another aspect, the apparatus further comprisesmeans for monitoring the load on the bearing.

A further aspect of the invention is a method for providing a load on abearing having an inner race mounted to a shaft and the bearing retainedon the shaft by a nut, the method comprising mounting a rod to an end ofthe shaft; without removing the nut, mounting a means for compressingthe inner race of the bearing to the shaft; and actuating the means forcompressing the inner race to compress the inner race to provide theload to the bearing. In one aspect, the means for compressing the innerrace comprises an adapter having a plate and a plurality of extensionsmounted to the plate, wherein mounting the means of compressingcomprises mounting the adapter to the rod and the inner race.

A still further aspect of the invention is a fastener arrangement forretaining a bearing on a shaft, the bearing having an inner bearing racehaving an outer diameter, the fastener arrangement adapted to permit abearing loading device to contact the inner bearing race, the fastenerarrangement comprising a first threaded ring adapted to threadably mountto the shaft and engage the inner bearing race, the first threaded ringhaving an outer diameter less than the outer diameter of the innerbearing race and an outer surface engagable by a tool; a second ringadapted to mount to the shaft and engage the first ring and engage theshaft to prohibit relative movement between first ring and the shaft;and a third threaded ring adapted to threadably mount to the shaft andto contact the second ring, the third ring having an outer surfaceengagable by a tool; wherein when the first ring, second ring, and thirdring are mounted to the shaft, the bearing is retained on the shaft andthe inner bearing race is exposed and can be contacted by the bearingloading device. In one aspect, at least one of the first threaded ringand the third threaded ring comprises a threaded nut.

An even further aspect of the invention is a method for providing a loadto a bearing having an inner race mounted to a threaded shaft, the innerrace having an outer diameter, the method comprising threading a firstthreaded ring onto the threaded shaft whereby the threaded ring contactsthe inner bearing race, the first threaded ring having an outer diameterless than the outer diameter of the inner; mounting a second ring to theshaft, the second ring adapted engage the first ring and engage theshaft to prohibit relative movement between first ring and the shaft;and threading a third threaded ring on to the shaft, the third threadedring adapted to engage the second ring; and engaging the inner race withan apparatus adapted to provide the load to the inner race. In oneaspect, the method further comprises monitoring the load on the innerrace. In another aspect, the method further comprises, when the load onthe inner race reaches about a predetermined load, tightening the firstthreaded ring against the inner race, for example, to maintain thepredetermined load on the inner race.

These and other aspects, features, and advantages of this invention willbecome apparent from the following detailed description of the variousaspects of the invention taken in conjunction with the accompanyingdrawings

BRIEF DESCRIPTION OF THE DRAWINGS

The subject matter, which is regarded as the invention, is particularlypointed out and distinctly claimed in the claims at the conclusion ofthe specification. The foregoing and other objects, features, andadvantages of the invention will be readily understood from thefollowing detailed description of aspects of the invention taken inconjunction with the accompanying drawings in which:

FIG. 1 is perspective view of a wheel hub assembly having a bearingpreloading apparatus according to one aspect of the invention.

FIG. 2 is a right side elevation view of the hub assembly shown in FIG.1.

FIG. 3 is a right side elevation view, partially in cross section, ofthe assembly shown in FIG. 1

FIG. 4 is a detailed view of the means for providing a preload shown inFIG. 3 and identified by detail 4.

FIG. 5 is a partial cross sectional view of another aspect of theinvention for transferring a load to a bearing.

FIGS. 6A, 6B, and 6C are partial axial elevation views of another aspectof the invention as viewed along the section lines 6-6 shown in FIG. 4with the addition of a typical tool according to one aspect of theinvention.

FIG. 7 is a right side elevation view, partially in cross sectional, ofanother aspect of the invention.

FIG. 8 is perspective view of a wheel hub assembly having a bearingpreloading apparatus according to another aspect of the invention.

FIG. 9 is a right side elevation view of the hub assembly shown in FIG.8.

FIG. 10 is a right side elevation view, partially in cross section, ofthe assembly shown in FIG. 8

FIG. 11 is a detailed view of the means for providing a preload shown inFIG. 10 and identified by detail 11.

FIG. 12 is perspective view of the bearing loading adapter shown in FIG.11.

FIG. 13 is a side elevation view, partially in cross section, of thebearing loading adapted shown in FIG. 12.

FIG. 14 is top plan view of the bearing loading adapter shown in FIG.12.

FIG. 15 is a perspective view of an axle nut according to another aspectof the invention.

FIG. 16 is a side elevation view, partially in cross section, of theaxle nut shown in FIG. 15.

FIG. 17 is a side elevational view, partially in cross section andsimilar to FIG. 11, of an apparatus for applying or verifying a preloadon a bearing according to another aspect of the invention.

FIG. 18 is a perspective view, partially in cross section, of a nutarrangement shown in FIG. 17 according to another aspect of theinvention.

FIG. 19 is an exploded perspective view the nut arrangement shown inFIGS. 17 and 18.

FIG. 20 is a plan view of an axle nut according to another aspect of theinvention.

FIG. 21 is a perspective view of a lock nut system which includes a locknut having a keeper and a keeper retaining member engaged with the nut.

DETAILED DESCRIPTION OF THE INVENTION

FIG. 1 is perspective view of a wheel hub assembly 10 having a bearingpreloading apparatus 20 according to one aspect of the invention. InFIG. 1, some of a section of the hardware has been removed to revealinner structure to facilitate disclosure of the invention. FIG. 2 isright side elevation view of the wheel hub assembly 10 and preloadapparatus 20 shown in FIG. 1. FIG. 3 is a right side elevation view,partially in cross section, of the assembly shown in FIG. 1. For thesake of illustration, the wheel assembly that would typically be mountedto wheel hub assembly 10 is omitted. Wheel hub assembly 10 represents atypical wheel hub that may be found on any wheeled vehicle, for example,a wheel hub of truck, a front or rear axle of a tractor of atractor-trailer, or an axle of a trailer.

The wheel hub assembly 10 shown in FIG. 1 is an assembly that wouldtypically be found on a front or rear axle of a cab or tractor of atractor-trailer, or an axle of a trailer. However, aspects of theinvention are not limited to use for vehicle bearings. As will generallybe understood by those skilled in the art, aspects of the invention maybe used to service bearings and bearing assemblies in any machine ordevice that employs bearings, including, but not limited to: powertrains, transmissions, machine components, on and off-road vehicles,aircraft wheels, marine drives, spacecraft, conveyor rolls, andwindmills, among others. According to aspects of the present invention,preloading apparatus 20 may be used in these and any other assembly forwhich bearing preload and/or endplay is desired, for example, anyassembly that utilizes thrust and radial load carrying bearings that areindirectly mounted.

As shown in FIGS. 1 and 3, typical wheel hub assembly 10 includes awheel hub or, simply, a hub 12, a threaded shaft, axle, or “spindle” 14.As is typical, on spindle 14 are mounted two antifriction bearings 16and 18 and spindle 14 includes an exposed end 13, which is typicallythreaded. Spindle 14 typically includes a retaining nut 11 threaded tothe exposed end 13. Retaining nut 11 may comprise the locking nutdisclosed in commonly owned copending U.S. application Ser. No.11/029,531 filed on Jan. 5, 2005, the disclosure of which isincorporated by reference herein, or any other available retaining nut.In the conventional art, retaining nut 11 typically is used to secure awheel (not shown) or hub assembly to a non-rotating axle 14. However, inaspects of the present invention, retaining nut 11 may be useful invarying the preload and/or endplay of bearings 16 and 18. Thoughbearings 16 and 18 are illustrated as tapered roller bearings, aspectsof the invention may be applied to other types of antifriction bearingsfor which it is desirable to provide preload and/or endplay, forexample, spherical roller bearings, deep groove ball bearings, and thelike. In the following discussion and claims, bearing 16 may be referredto as the “outboard bearing” and bearing 18 may be referred to as the“inboard bearing.”

As shown in FIG. 3, as is typical of bearings, outboard bearing 16includes an inner race (or cone) 15, an outer race (or cup) 17, aplurality of rollers 22, and a roller cage 24. Similarly, inboardbearing 18 includes an inner race (or cone) 19, an outer race (or cup)21, a plurality of rollers 26, and roller cage 28. As shown in FIG. 3,the outer race 17 of outboard bearing 16 is positioned, for example, aninterference fit, into a annular cavity 29 having a annular retainingflange 30. Similarly, the outer race 21 of inboard bearing 18 ispositioned into an annular cavity 31 having a retaining flange 32. Also,the inner race 15 of outboard bearing 16 is positioned, for example, asliding fit, onto the outside diameter of spindle 14 and the inner race19 of inboard bearing 18 is positioned against a shoulder 34 of spindle14, which may be a sliding or interference fit to the spindle diameter.As such, any loads applied to hub 12 or spindle 14 are transferred toinboard bearing 18.

According to some teachings in the art, outboard bearing 16 and inboardbearing 18 can be provided with at least some preload to enhance theperformance or bearing life and the performance or life of wheel hubassembly 10. For example, as described in the Timken Tech Tip, Volume 6,Issue 3 (copyrighted 2001) entitled “Preload in WheelBearings”[http://www.timken.com/products/bearings/techtips/PDFs/Vol6No3.pdf#search=‘Bearing%20Preload’],

-   -   Slight preload [on wheel bearings] can improve bearing, seal,        and tire life, but only if the entire process is in control. “In        control” means that you actually know the bearing setting        process will result in a consistent bearing setting range.        The Tech Tip continues,    -   Unfortunately, neither dial indicators nor any other standard        tool will tell a technician the amount of preload in a wheel end        . . . . To date, there isn't anything available that will        confirm that the bearing fastener is providing the correct        preload setting.” [Emphasis added.]        In other words, one of the leading bearing suppliers in the        world believes that conventional torquing methods and dial        indicator methods have proven to be unsatisfactory means of        providing preload and endplay. Specifically, prior art methods        have been shown to provide unreliable and non-repeatable        preloads and/or end play to bearings such as bearings 16 and 18.        Moreover, such experts in the field contend that “there isn't        anything available” that can confirm a bearing preload. However,        the preload assembly 20 according to aspects of the present        invention provides such a device—a reliable, accurate, and        repeatable means of providing preload and/or endplay adjustment        to bearings such as bearings 16 and 18. In addition, aspects of        the invention provide means for monitoring the preload on the        bearings to, for example, ensure that the desired preload is        provided, in contrast to the unreliable and often inaccurate        assumed preloading of the prior art.

As shown in FIGS. 1-3, preload assembly 20 includes a rod or shaft 40mounted for rotation within a housing or frame 42, and a means 44 forcompressing hub 12 against the outer race 21 of inboard bearing 18, inwhich the means 44 for compressing is mounted to rod 40. Means 44,through housing 42 and hub 12, provides a known and predeterminedpreload to bearing 18. Housing 42 may be referred to as “the shoe” or“the foot” of preload assembly 20. Rod 40 is adapted to attach to theexposed end 13 of shaft 14, for example, by means of collar 46, thoughother attachment means may be used. Means 44 may be mounted to rod 40 bymeans of adjustment nut 48 which may be threaded to rod 40 and provide acompressive load to means 44. Nut 48 may be adapted to facilitaterotation of nut 48, for example, nut 48 may include arms 50 or a handwheel that can assist a mechanic while manually tightening oruntightening nut 48. In one aspect, nut 48 may be adapted to be rotatedby an automated tool, for example, a drill or stepper motor. Forinstance, nut 48 may be fashioned with a hex head or threads to engagean automated tool, for example, a torque motor. One such automated toolis disclosed in FIG. 7, discussed below.

Means 44 may be any means that is adapted to transfer the compressiveload provided by nut 48 to hub 12 and outer bearing race 21 of bearing18. In one aspect, means 44 may simply comprise an extension of housing42 whereby nut 48 contacts and compresses housing 42 against hub 12,though, absent a means to monitor the load transmitted, such a systemwould not be as advantageous as other aspects of the invention. Inanother aspect of the invention, means 44 is not only adapted totransfer a load from but 48 to outer race 21, but means 44 also providesa means for monitoring the compressive load transferred, for example,some means of direct or indirect indication of the load transferred toouter race 21, that is, the preload on bearing 18.

In one aspect of the invention, the indication of the compressive loadtransferred through means 44 may be provided mechanically, for example,by means of compression springs having a known spring constant, forexample, coil springs or disc springs, and a deflection indicator, forexample, a dial indicator, as is known in the art. In this aspect, thedial indicator may be mounted to detect and indicate the compression ofone or more springs positioned in means 44 due to the advancement of nut48, and the compression load calculated from the deflection indicatedand the known spring constant of the springs used. This aspect of theinvention may provide a reliable and repeatable means for monitoring thepreload provided to bearing 18.

In another aspect of the invention, means 44 may provide an indicationof the compression load transferred by nut 48 electronically, forexample, by means of a load or pressure sensor, for instance, one ormore strain gages or load cells positioned in means 44. In this aspectof the invention, the load sensor may be wired to an appropriateprocessor and display to, for example, provide a digital readout of thecompressive load to the mechanic operating preload device 20. Thetransmission of signals from the sensor may also be practicedwirelessly, for example, by means of an RF signal. This aspect of theinvention may also provide a reliable and repeatable means formonitoring the preload provided to bearing 18.

In another aspect of the invention, means 44 may include at least onefluid, for example, a gas, such as air; or a liquid, such as, water,oil, or hydraulic fluid, the pressure of which can be detected andmonitored, for example, by means of a pressure gage, pressure sensor, ora mechanical indicator. In one aspect, the fluid pressure may comprisethe source of compressive load on bearing 18. One apparatus that may beused to effect this aspect of the invention is shown in FIG. 7. Thefluid may be retained in a cavity for example, a deformable cavity, suchas a bladder or hose, for example, an air spring; or a cavity havingrigid walls and at least one moveable wall, for example, as in acylinder and piston. In one aspect, the deformable cavity or air springmay be made of molded rubber, somewhat like an inner tube, and theconfiguration of means 44 may be adapted accept the molded rubber wheninflated and deflated.

When air is used as the fluid, the air may be provided by conventional“shop air” at a pressure of about 100 psig. The pressure of the fluid inthe deformable cavity may be monitored by means of sensor or pressuregage, for example, a pressure gas mounted to a nozzle inserted the wallof the deformable or non-deformable cavity. In one aspect, a mechanicalindicator may be activated, for example, a lever deflected when thedesired fluid pressure in means 44 is reached advising the mechanic. Oneaspect of the invention having a means 44 having a fluid is illustratedin FIGS. 1-3. FIG. 4 is a detailed view of the means 44 for providing apreload shown in FIG. 3 and identified by detail 4.

In the aspect of the invention shown in FIG. 4, means 44 comprises ahousing 52 and a movable piston 54 mounted for axial movement in housing52. In this aspect of the invention, an internal cavity 56 is providedin housing 52 between the between housing 52 and piston 54, for example,an annular cavity. Internal cavity 56 is at least partially filled, forexample, substantially completely filled, with a fluid, for example, agas, air, oil, water, and the like, that produces a hydrostaticpressure, P, when housing 52 is compressed by the advancement of nut 48on rod 40. Piston 54 may be provided with one or more seals 61 and 63,for example, one or more wiper seals, to minimize or prevent the leakageof fluid from cavity 56. Also, housing 42 may include an internal cavity57, which provides clearance for the displacement of piston 54 withinhousing 52. In one aspect, a leakage path through housing 52 may beprovided from cavity 57 to minimize or prevent buildup of fluid incavity 57 which may interfere with the proper operation of piston 54.Piston 54 may also be retained in housing 52 by means of a retainer orsnap ring 55. Housing 52 and piston 54 may be fabricated by machiningfrom solid bar or plate stock, welded from bar or plate, forged, orcast.

As shown in FIG. 4, the compressive load applied by the advancement ofnut 48 is transmitted to housing 52, to the fluid in cavity 56, topiston 54, to cylindrical housing 42, to hub 12, and ultimately to theouter race 21 of bearing 18. Thus, according to aspects of theinvention, the hydrostatic pressure induced in the fluid in the cavity56 by the advancement of nut 48 provides a direct indication of thepreload on bearing 18.

In one aspect, the pressure P in cavity 56 may be monitored, forexample, continuously, by means of a pressure sensor or pressure gage.As shown in FIG. 4, pressure P in cavity 56 may be monitored by one ormore pressure indicators 60 which is adapted to detect the pressure P incavity 56 via a passage 58 in housing 52. Pressure indicator 60 may bean analog or digital pressure gage. Pressure indicator 60 may be apressure sensor adapted to detect the pressure P in cavity 56 andforward an electrical signal corresponding to the pressure P to aprocessor or controller adapted to display the pressure, record thepressure, energize a circuit in response to the pressure, and/or providea signal to the mechanic, for example, a tone or bell that a pressurecorresponding to a desired preload on bearing 18 has been achieved.

According to aspects of the invention, the pressure P and thecorresponding geometry (for example, the inside and outside diameters ofcavity 56) may be used by a mechanic to determine the preload on bearing18. For example, for a desired preload L (in pounds, Newtons) and agiven area of piston 54 exposed to pressure P (in square inches, squaremeters), the desired pressure of the fluid in cavity 56 may bedetermined by the equation P=L/A, for example, in psi or Pascal. Forexample, when a preload of 6000 pounds lbs. (L) is desired to provide ancompressive deflection of 0.003 inches on bearing 18, and the outsidediameter of annular cavity 56 is 3 inches and the inside diameter ofcavity 56 is 1 inch, the target pressure, P, is calculated byP=L/A=(6000 lbs)/((π/4)(3²−1²))=6000 lbs/(2π in²)=955 psig.  Equation 1This pressure may now be used as the target pressure in cavity 56 anddetected by pressure indicator 60 to provide the desired 0.003-inchcompressive deflection for bearing 18. According to aspects of thepresent invention, the pressure of the fluid in cavity 56 may bemonitored to determine when the desired pressure P is achieved whereinthe desired preload is provided to bearing 18.

In one aspect of the invention, one or more antifriction bearings may beprovided for means 44. For example, in one aspect, one antifrictionbearing 62 may be positioned between nut 48 and housing 52 and anotherantifriction bearing 64 may be located between piston 54 and housing 42.Bearings 62 and 64 may be roller-type bearings or reduced frictionmaterial bearings. For example, bearings 62 and 64 may comprise needlebearings or a material containing at least some PTFE, for example,DuPont's Teflon® PTFE or Saint-Gobain's Rulon® PTFE, or theirequivalent. Bearings 62 and 64 may be retained by one or more retainingdevices 65 and 66, for example, one or more snap rings.

As shown in FIGS. 1-4, housing or frame 42 is adapted to transmit thecompressive load provided by the advancement of nut 48 to hub 12. In oneaspect, housing 42 may be any structure adapted to transmit this loadwhile not interfering with the movement and operation of nut 11 andcollar 46. In one aspect, housing or frame 42 comprises a cylindricalhousing and may include at least one opening to permit access to nut 11and collar 46, for example, for servicing by a mechanic. In the aspectof the invention shown in FIGS. 1-4, housing 42 comprises an upperflange 70 adapted to receive the force transmitted by means 44, a lowerplate or ring 72 adapted to transmit a load to hub 12, and a pluralityof posts 74 spaced about flange 70 and ring 72 to transmit a loadbetween flange 70 and ring 72. In one aspect, flange 70 may be any plateadapted to engage piston 54 and posts 74. Ring 72 may be any annularplate adapted to receive a load from posts 74. In one aspect, theinterface between ring 72 and hub 12 may be provided with anantifriction bearing, for example, a needle bearing or a PTFE-containingmaterial, as described above with respect to bearings 62 and 64. Posts74 may comprise cylindrical posts, for example, circular cylindrical orrectangular cylindrical, extending from flange 70 to ring 72. Whenhousing 42 is provided as a cylindrical body, posts 74 may comprisesections of the cylindrical body remaining when openings are introducedto the cylindrical body. In one aspect, ring 72 may be omitted whereinposts 74 contact the surface of hub 12 directly. When ring 72 isomitted, posts 74 may be provided with means to reduce friction betweenthe ends of post 74 and hub 12. For example, the ends of posts 74 may beadapted to provide antifriction bearings or rollers or reduced frictionmaterials, such as, a PTFE-containing material. Housing 42 may bemachined from stock shapes, assembled by means of fasteners, fabricatedby welding, forging, casting, or a combination thereof.

In one aspect of the invention, housing or frame 42 may be adapted tocontact the inner race of outboard bearing 16, that is, instead ofcontacting hub 12, and transmit a preload to bearing 18. For example,with reference to FIG. 3, in some wheel hub assemblies 10, the diameterof retaining nut 11 may be smaller than the diameter of inner race 15 ofoutboard bearing 16 whereby access to inner race 15 is not obstructed bynut 11. (In FIG. 3, the diameter of nut 11 is greater than the diameterof inner race 15 and thus inner race 15 cannot be directly accessed.)Under this condition, housing 42 may be sized or adapted to contact theinner race 15 whereby the compression load providing by advancing nut 48may be transmitted to outboard bearing 16 via inner race 15 and frombearing 16 to hub 12 and to outer race 21 of inboard bearing 18. Thatis, according to one aspect of the invention, a preload may betransferred to inboard bearing 18 by means of compression on the face ofhub 12 or on the inner race 15 of bearing 16. In one aspect, compressivedeflection is imposed on both of bearings 16 and 18.

According to aspects of the invention, the compressive load transmittedto the bearing 18 is transmitted through hub 12. Therefore, at leastsome of the compressive deflection provided by the present inventionwill comprise deflection of hub 12. Therefore, in some aspects of thepresent invention, when determining the compressive deflection ofbearing 18 under preload, the deflection of hub 12 may also beconsidered. For example, a dial indicator mounted on, for example,housing 42 to detect the compression deflection of bearing 18 may alsodetect the deflection of hub 12, depending upon the magnitude of theload and the stiffness of hub 12. In one aspect of the invention, whendeflection of hub 12 may effect the compressive deflection, thedeflection measured can be normalized to or compensated for the hubstiffness, that is, hubs of varying stiffness may have varyingdeflections though the corresponding compressive deflection of bearing18 will be substantially the same. However, any deflection of hub 12will likely have little effect upon the compressive force transmitted tobearing 18.

It will be apparent to those of skill in the art that the design ofhousing 42 may be modified whereby housing 42 may contact inner race 15.For example, flange 70 and ring 72 may be reduced in diameter wherebyring 72 may contact inner race 15. This alternative aspect of theinvention is shown FIG. 5. FIG. 5 illustrates a partial cross sectionalview of an alternate design of housing 42 for transferring thecompressive load from means 44 to bearing 18 via inner race 15 ofoutboard bearing 16. In this aspect, the size of nut 111 on spindle 14is smaller than nut 11 shown earlier, whereby an inner race 15 isexposed and can be contacted by a modified housing 142. Inner race 15,bearing 16, and hub 12 are shown in FIG. 5 for reference. In this aspectof the invention, the diameter of upper flange 70 is reduced to thediameter of upper flange 170 shown in FIG. 5, the diameter of ring 72 isreduced to the diameter of ring 172 shown in FIG. 5, and posts 74 arereplaced with posts 174. As a result, the compressive load can betransferred to inner race 15 of bearing 16. In another alternativedesign of housing 42, posts 74 may be angled or tapered inward towardthe centerline of the assembly and the diameter of ring 72 reducedaccordingly whereby ring 72 may contact inner race 15. Othermodifications to housing 42 to achieve this contact with inner race 15will be apparent to those of skill in the art.

As discussed previously, rod 40 is adapted to attach to the exposed end13 of spindle 14. Though this may be effected by many conventionalmeans, including welding and mechanical fasteners, in the aspect of theinvention shown in FIGS. 1-4, rod 40 is attached to end 13 of spindle 14by means of a collar 46. In the aspect shown, collar 46 is mounted torod 40 by means of internal threads 47 in collar 46 that thread ontoexternal threads 49 on rod 40. Collar 46 also includes a second set ofinternal threads 45 that engage external threads 51 on spindle 14. Inone aspect, only 2 or 3 external threads 51 need be engaged by collar46. According to one aspect, multiple collars 46 having varyingdiameters may be provided to accommodate varying diameters of spindle14. Each of these collars 46 may be adapted to engage external threads49 on rod 40. In one aspect, the movement of rod 40 may be limited by acollar or ring 76, for example, a snap ring, mounted on rod 40.

Rod 40, housing 42, collar 46, nut 48, arms 50, housing 52, piston 54,and housing 42 may be fabricated from any conventional structural metal,for example, iron, steel, stainless steel, aluminum, titanium, nickel,magnesium, brass, or bronze, among others.

In one aspect of the invention, apparatus 20 may be used to apply andmonitor a preload to inboard bearing 18. In a typical procedure, thewheel (not shown) mounted to hub assembly 10, for example, mounted tostuds on hub 10, as exemplified by stud 100 in FIG. 3. As shown in FIG.4, apparatus 20 may be prepared by assembly and filling cavity 56 with afluid, for example, oil, through one of the access ports 58 that is notoccupied by pressure indicator 60. Nut 11 may be loosened or handtightened prior to mounting apparatus 20, though any light load on nut11 will typically be relieved with application of tension to spindle 14by means of rod 40. Apparatus 20 is then mounted to hub assembly 10 byattaching rod 40 to spindle 14 by means of collar 46. As a result,housing 42 is brought into contact with hub 12. Assuming a desiredcompressive deflection for bearing 18, for example, 0.003 inches, and acorresponding preload, L, the desired target pressure in cavity 56 canbe calculated by Equation 1.

The loading of bearing 18 is initiated by advancing, that, istightening, nut 48, against housing 52 via bearing 62, for example, bymeans of arms 50. The build up of pressure in cavity 56 as indicated bypressure indicator 60 may be monitored by the mechanic. The tighteningof nut 48 continues until the target pressure is achieved. The hubassembly may be rotated at least once to provide proper seating of therollers in bearing 18. Once the target pressure is achieved in cavity56, and the desire preload is applied to bearing 18, nut 11 may betightened against inner race 15 to maintain the preload after apparatus20 is removed. The desired tightening of nut 11 may be determined bymonitoring the pressure in cavity 56 on pressure indicator 60. Forexample, should the pressure begin to decrease during tightening of nut11, the nut may be tightened too much. The reduction in pressure meansthat the preload on bearing 18 is being relieved and transferred to nut11 by the tightening of nut 11. In one aspect of the invention thetightening of nut 11 can proceed until a decrease in pressure isobserved. At that point, the tightening of nut 11 may be stopped, or nut11 may be untightened slightly, for example, about ⅛ turn. Again, thehub assembly may be rotated at least once to provide proper seating ofthe rollers in bearings 16 and 18. Upon completion of the preloading,apparatus 20 may be removed from wheel hub assembly 10 and, for example,the wheel remounted. Variations on this procedure while not deviatingfrom the desired results may be apparent to those of skill in the art.

In another aspect of the invention, apparatus 20 may be used to adjustthe endplay of a bearing. For example, in some bearing installations itis desirable to create an endplay for a bearing assembly, for example,an endplay of between about 0.001 inches and about 0.003 inches. Forinstance, see undated instructions entitled “ProTorq® Advanced AxleSpindle Nuts” flyer by Stemco, of Longview, Tex. Although proceduressuch as these which apply specified torques to the nut are intended toprovide the specified endplay in the bearing, the inventor has foundthat the actual endplay provided by such procedures may varydramatically. For example, the actual axial deflection of the bearingsthat results from the applied torque may vary due to, among otherthings, differences in torque resistance (or friction) between matingsurface, for example, between nut 11 and the axle threads 15 and betweenthe face of nut 11 and the surface of bearing 16, among others. Furthererrors may be introduced by such torque-based procedures by misalignmentof the bearing rollers that may occur in between steps in the specifiedprocedures. Therefore, there is a need in the art to provide an accurateand repeatable means of providing bearing endplay. One aspect of theinvention addresses this need.

Aspects of the present invention eliminate the inaccuracies that areinherent in prior art endplay adjustment procedures and can be used toprovide accurate end play settings of as fine as 0.001 inches and 0.002inches. With reference to the cross section shown in FIG. 3, one methodof providing accurate endplay adjustment includes the following steps.Starting with a greased and assembled wheel end assembly 10 (thisprocedure may be practiced with or without the wheels present), nut 11is unloosened or installed and only fastened hand tight. The apparatus20 shown in FIG. 1-4 is then mounted to the wheel hub assembly 10.Specifically, rod 40 having means 44, which comprises a fluid-containinghousing 52, is attached to axle 14 by means of collar 46, and housing 42is mounted to hub 12. In this aspect of the invention, the fluid inhousing 52 is assumed to be hydraulic fluid. According to thisprocedure, nut 48 is rotated and advanced, for example, by means of arms50 to produce a target hydraulic fluid pressure of, for example, 1000psig, in cavity 56 as indicated by pressure indicator 60, for example,an analog pressure gage. The target pressure is typically predeterminedby Equation 1 and the desired compressive deflection or endplay desiredin bearing 18. The target pressure will vary depending upon the size andtype of bearings used and the size of cavity 56, among other things.

The wheel hub assembly 10 is then rotated about spindle 14 at least onecomplete revolution, typically, at least three complete revolutions, toseat the rollers in inboard bearing 18. (See Timken Tech Tip Volume 1,Number 6 entitled “Why oscillate or rotate a bearing”http:://www.Timken.com/products/bearings/techtips/tip6.asp, thedisclosure of which is incorporated by reference herein.) The pressureindicated by the pressure indicator 60 (that is, about 1000 psig) mayvary as rollers 26 of inboard bearing 18 are seated by the rotation. Ifthe pressure in cavity 56 deviates from the desired target pressure, thepressure in cavity 56 may be re-established by rotating nut 48, forexample, by means of arms 50. The rotation of wheel assembly 10 aboutspindle 14 and the repressurization step may be repeated until rollers26 of inboard bearing 18 are properly seated and the pressure indictedby pressure indicator 60 stabilizes to about the target pressure. It isunderstood that there may be slight variation in the pressure in cavity56 due to slight misalignments (that is, the out of “squareness”) of theinstalled bearing, among other things. The rollers 26 of inboard bearing18 are then substantially seated in inner race 19.

Next, with the inboard bearing 18 properly seated by the aboveprocedure, the endplay in outboard bearing 16 may be adjusted. While thetarget pressure (again, for example, about 1000 psig) is maintained inhousing 52, nut 11 is rotated and tightened, for example, with a handheld wrench, on spindle 14, for example, slowly. During or after thetightening of nut 11, wheel assembly 10 is rotated about spindle 14whereby rollers 22 of outboard bearing 16 are seated in inner race 15.The nut 11 is continued to be tightened until the pressure indicted bypressure indicator 60 just begins to drop. This drop in pressureindicates that the preload on inboard bearing 18 is being relieved bythe compression of nut 11 against inner race 15 of outboard bearing 16.Nut 11 is then loosened slightly to so that the target pressure isregained, and thus the preload on inboard bearing 18 is reestablished,that is, typically, without retightening nut 48. This condition ofadjustment, where the desired preload is established in the inboardbearing 18 and the compression of nut 11 on inner race 15 is such thatany further tightening will unload the preload on inboard bearing 18,according to one aspect of the invention, is referred to as “the loadreference point.” Practicing aspects of the present invention, this loadreference point can be fairly easily identified by feel by a mechanic.According to the invention, at this load reference point, the rollers inboth outboard bearing 16 and inboard bearing 18 are properly seated anddesired preload (that is, due to the 1000 psig pressure in housing 52)is applied to outer race 21 of inboard bearing 18.

According to aspects of the invention, a method and an apparatus areprovided by which the mechanic can accurately determine the loadreference point for a bearing assembly. Aspects of the present inventionare not prone to the variability of the preload due to the unknown andunpredictable frictional forces between mating surfaces, regardless ofwhat the desired bearing preload and/or endplay setting. According toaspects of the invention, after establishing the neutral point position,the mechanic may relatively easily provide the desired adjustment of nut11 that accurately achieves the desired bearing preload and/or endplaysetting.

As is known in the art, a known preload, for example, the 6000 pounds inthe example above, results in a known value of axial compression of abearing, for example, an axial compression of 0.004 inches. According toaspects of the invention, in the load reference point position, whereboth bearings are correctly aligned and at zero preload on nut 11, thepreload on inboard bearing 18 will be captured by or transferred to nut11 if nut 11 is loosened, for example, precisely 0.004″ from the loadreference point. Therefore, according to aspects of the invention, thepreload may be varied or the endplay provided by precisely controllingthe rotation of nut 11. One aspect of the present invention provides amethod and apparatus for controlling the rotation of nut 11 to provide adesired preload or endplay.

According to one aspect of the invention, a method and a apparatus isprovided of employing a calibrated wrench that can be used to accuratelycontrol the rotation of nut 11 to provide a desired preload or endplay.This method and apparatus are illustrated in FIGS. 6A, 6B, and 6C. FIGS.6A, 6B, and 6C are partial axial elevation views of the apparatus 20 asviewed along the section lines 6-6 shown in FIG. 4 with the addition ofa wrench 90. For ease of illustration, FIGS. 6A, 6B, and 6C onlyillustrate the portion of housing or frame 42, specifically ring 72 andposts 74. These figures also illustrate the end of shaft 14 and nut 11mounted on shaft 14.

According to one aspect of invention, wrench 90 includes a handle 89 andtwo opposing tines 92 spaced to engage the opposite flats on nut 11.Wrench 90 also includes at least one recess 94 positioned between tines92. Recess 94 includes two opposing end surfaces 91, 93 adapted tocontact a post 74 and function as stops to the movement of wrench 90. Inone aspect, stops 91, 93 may be provided by one or more projections orbosses between tines 92 instead of one or more recesses 94. In anotheraspect, the stopping surfaces may be provided by the closed ends of oneor more slots 95 (shown in phantom) in ring 72 that are adapted toreceive one or more pins 97 (also shown in phantom) projecting frombeneath wrench 90. The one or more slots 95 may vary in length tocorrespond to one or more angular rotations. Other adaptations of wrench90 and/or ring 72 and posts 74 may be provided to provide the desiredlimitations in the rotation of nut 11. Wrench 90 may have a thicknessranging from about 0.50 inches to about 1 inch or more.

As shown in FIG. 6A, recess 94 may have a common centerline with handle89; however, recess 94 may be located anywhere between tines 92. In oneaspect, a plurality of recesses 94, for example, 3 or more recesses 94,may be provided in wrench 90. According to one aspect of the invention,the arc length separating the opposing ends 91, 93 of recess 94 isprovided to limit the rotation of wrench 90 when wrench 90 is used torotate nut 11 to provide the desired preload or end play. This aspect ofthe invention is more clearly illustrated by describing one procedurethat may be used as shown in the sequence of steps illustrated by FIGS.6A, 6B, and, 6C.

In this example, the size of the recess 94 in handle 90, that is, thearc length between the ends 91, 93 of recess 94, is provided whereby therotation of wrench 90 provides a predetermined angular displacement, α.(As will be discussed below, this angular displacement, α, may bedetermined from the desired preload or endplay and the pitch of thethreads on spindle 14.) As shown in FIG. 6A, wrench 90 may be mounted tonut 11 whereby tines 92 engage opposing flats of nut 11 and recess 94accepts one of the posts 74 of housing 42. As shown in FIG. 6B, theengaged wrench 90 and nut 11 are held fixed by holding handle 89 and hub12 is carefully rotated in a clockwise direction as indicated by arrow96 until one end 91 of recess 94 contacts a post 74. This contacting ofend 91 of recess 94 upon post 74 establishes the base position for thisangular adjustment of nut 11.

Now, as shown in FIG. 6C, hub 12 is fixed from further rotation, wrench90 is rotated in a counter-clockwise direction—as indicated by arrow98—whereby the opposite end 93 of recess 94 contacts post 74, and thusthe rotation of nut 11 is limited to the arcuate spacing between theends 91, 93 of recess 94. Since the wheel hub 12 is typicallysubstantially more massive than wrench 90 and nut 11, hub 12 may simplybe retained by hand, or other means, while rotating wrench 90 and nut111. However, due to the relative inertia of hub 12, it may not benecessary for the mechanic to restrain hub 12 while rotating wrench 90and nut 11, while ensuring that rotation of the wrench is stopped whenend 93 contacts post 74.

It will be apparent to those of skill in the art that the desiredangular rotation a of nut 11 is not the arcuate length between ends 91and 93 of recess 94, but, due to the diameter of posts 74, the desiredangular rotation a corresponds to the arcuate length between the centerof posts 74 before and after rotation.

One example of the use of the method and apparatus described withrespect to FIGS. 6A, 6B, and 6C, is illustrated by the followingexample. This example assumes that the wheel hub assembly 10 has beenadjusted whereby a compression of bearing 18 has been established of,for example, 0.004 inches, and bearings 16 and 18 are in their “loadreference point.” It is also assumed that the desired endplay of bearingsupports 16 and 18 is 0.001 inches and the threads on nut 11 and shaft14 have a pitch of 12 threads per inch (that is, 1/12 inches perrevolution), which is a common pitch for truck axles. The total requireddisplacement of nut 11 to overcome the preload compression and obtainthe desired endplay is 0.004+0.001=0.005 inches. For a 12 pitch thread,the required rotation of nut 11 is (0.005 inches)/( 1/12inches/revolution)=0.060 revolutions of nut 11 to provide the desiredendplay, which corresponds to (0.060 revolutions)×(360degrees/revolution)=21.6 degrees. For a typical spindle thread pitch of12 threads per inch, an accuracy of 0.001 inches relates to more thatfour degrees of rotation of nut 11 or wrench 90, and that relates to anexcursion of more than an eighth of an inch at the radial distance wherepost 74 is located. Therefore, by fabricating the recess 94 of handle 90whereby angle α is, for example, 21.6 degrees, wrench 90 can be used inthe procedure described above to provide the 0.001 inches of endplaydesired in this example. Other examples of the use of wrench 90 will beapparent to those of skill in the art.

FIG. 7 illustrates a right elevation view, partially in cross section,of another arrangement 110 according to another aspect of the invention.In this aspect, fluid pressure in means 44 may provide the compressiveload to bearing 18. In this aspect, of the invention, instead of thecompressive force provided by the advancing of a nut, such as nut 48 inFIG. 3, the compressive force provided by nut 48 may be supplemented byor replaced by the fluid pressure force provided to means 44, forexample, the fluid pressure provided to cavity 56 in housing 52 havingpiston 54. In this aspect, the fluid pressure may be provided by conduitor hose 200. Hose 200 may supply fluid, for example, hydraulic fluid,from a pressurized supply, for example, a pump. The fluid supplied tohose 200 may vary from 500 to 3000 psig. In one aspect, the fluidpressure provided through hose 200 may be the only supply of compressiveforce to bearing. In this aspect shown in FIG. 7, rod 40, shown in FIG.3, is replaced by rod 140. Similar to rod 40, rod 140 engages spindle 14as described in other aspects of the invention. However, contrary to rod40, rod 140 includes a knob 145 that restrains means 44, for example,through an antifriction bearing. Knob 145 may be knurled or include ahand wheel or one or more arms 50 similar to nut 48.

The aspect of the invention shown in FIG. 7 may be used to automaticallyregulate the compressive load on bearing 18, for example, by regulatingthe pressure introduced to means 44 through hose 200. In one aspect, theinvention may include an automatic controller, for example, a PIDcontroller, personal computer, or PLC controller adapted to regulate thepressure in hose 200. For example, the predetermined preload or endplayand the parameters of the bearing being loaded may be entered into thecontroller and, after mounting rod 140, housing 42 and means 44 to hub12, the controller may automatically ramp up the fluid pressure toprovide the desired preload or to verify an existing preload. The aspectof the invention shown in FIG. 7 may be suitable for production lineapplications, among others.

In one aspect, the fluid provided by hose 200 may be provided bypressure increasing device, for example, a pressure intensifier, thatis, a device that converts one pressure to a higher pressure. Forexample, the pressure-increasing device may be provided with a pressuresupply of, for example, 100 psig (for instance, shop air) and increasedto, for example, 2000 psig hydraulic fluid, which is then supplied tohose 200. Other sources of high-pressure fluid may be provided accordingto aspects of the invention.

It will also be understood that due to the variations in angle α thatmay be desired, for different bearings, different spindle pitches, anddifferent endplays and preloads, among other things, many differentwrenches 90 having recesses 94 of varying width may be provided. In oneaspect of the invention, a plurality of recesses 94 of varying width orangle α may be provided in handle 90. In another aspect of theinvention, recess 94 in handle 90 may be adjustable by the operator, forexample, the position of at least one end of recess 94 may be variableto provide for varying angles α. In another aspect, the width betweentines 92 if wrench 90 may be variable to permit use of wrench 90 on nuts11 of varying diameter. According to aspects of the invention, anadjustable wrench may be provided that can be calibrated for a desiredpreload and/or endplay values for a specific spindle and hub design.

Aspects of the invention may also be used to evaluate the preload orendplay on an existing bearing or bearing assembly. For example, anexisting truck hub assembly may be evaluated for its existing preloadand compared to the desired preload, and, if necessary, adjustedaccordingly. First, the truck may be jacked up, if needed. (The hub maybe allowed to cool, if necessary). Apparatus 20 may then be mounted tohub 12 and spindle 14 (with reference to FIG. 4) and the means 44actuated to introduce tension to spindle 14 and compression to hub 12.(The wheel may be mounted to removed.) The means 44 may be regulated to,for example, vary the fluid pressure, to gradually increase the preloadon bearing 18. While the load is increased, a mechanic can repeatedlycheck the load on or the “tightness” of nut 11. When nut 11 begins toloosen, the existing preload on bearing 18 has been met or exceeded. Acomparison of the actual preload indicated by means 44, for example, thefluid pressure, with the desired preload can then be made. Anyadjustments to the preload, either higher or lower, can be madeaccording to the procedures described above.

While one aspect of the present invention, in which the inboard bearing18 is loaded through hub 12, can provide a useful indication of thepreload present in bearings 16 and 18, for example, by assuming apredetermined distribution of load between bearing 16 and 18 anddistributing the preload measured on bearing 18 accordingly, otheraspects of the invention can provide an more accurate indication of thepreload on bearings 16 and 18. For example, the aspect of the inventionillustrated and described with respect to FIG. 5 above and the aspect ofthe invention illustrated and described with respect to FIGS. 8 through19 below, in which the loading of bearings 16 and 18 transmitted viabearing 16.

FIG. 8 is perspective view of a wheel hub assembly 201 having a bearingpreloading assembly 202 according to another aspect of the invention. Aswill be discussed more fully below, in contrast to the apparatusdiscussed above with respect to FIGS. 1-5, preloading assembly 202introduces a load to the outboard bearing 16, instead of to hub 12.According to this aspect of the invention, contact with the inner raceof the outboard bearing is accomplished by means of specially designedaxle nut or an axle nut arrangement. Unlike prior art methods anddevices, aspects of the invention permit mechanics to apply or confirm apreload to outboard bearing 16.

FIG. 9 is a right side elevation view of the hub assembly 201 shown inFIG. 8 and FIG. 10 is a right side elevation view, partially in crosssection, of the assembly shown in FIG. 8. FIG. 11 is a detailed view ofthe means for providing a preload shown in FIG. 10 and identified bydetail 11. FIGS. 8-11 are views similar to those shown in FIGS. 1-3 andinclude many of the structures shown in FIGS. 1-3, which are identifiedwith the same reference numbers that appear in FIGS. 1-3. Thesestructures may typically comprise the same structures having the sameproperties as those discussed above with respect to FIGS. 1-5. Forexample, hub assembly 201 in FIGS. 8-11 includes a hub 12, a threadedshaft, axle, or “spindle” 14, an outboard antifriction bearing 16, aninboard antifriction bearing 18. As shown in FIG. 10, outboard bearing16 includes an inner race (or cone) 15 and an outer race (or cup) 17,and inboard bearing 18 includes an inner race (or cone) 19 and an outerrace (or cup) 21.

As also shown in FIGS. 8-11, wheel hub assembly 201 includes preloadassembly 202 that, similar to preload assembly 20 shown in FIGS. 1-5,includes a rod or shaft 40 mounted to spindle 14 by means of collar 46,and a means 244 for providing a compressive load to bearing 16. Againsimilar to the aspects shown in FIGS. 1-5, means 244 of preload assembly202 shown in FIGS. 8-11 includes a nut 48 threaded to shaft 40. Nut 48may include arms 50 or a hand wheel to assist the operator in rotatingnut 48. Means 244 of preload assembly 202, similar to means 44 discussedabove with respect to FIGS. 1-5, may provide a compressive load tobearing 16 or means 44 may be any means that is adapted to transfer thecompressive load provided by nut 248 to the inner race 15 of bearing 16.In one aspect, means 244 provides a means for monitoring the compressiveload transferred, for example, some form of direct or indirectindication of the load transferred to inner race 15, as described abovewith respect to means 44, for example, by means of compression springs,electronically, or by means of a fluid pressure sensor, such as pressuregage 60.

According the aspect of the invention shown in FIGS. 8-11, thecompressive load of nut 48 and/or means 244 is transmitted to bearing16, and to bearing 18, by means of loading adapter 210. In one aspect,loading adapter 210 works in conjunction with modified axle nut 220 toprovide a load to inner race 15 of outboard bearing 16. As describedabove, for example, with respect to FIGS. 4 and 5, conventional axlenuts, for example, axle nut 11 in FIG. 5, are typically larger indiameter than inner race 15 of bearing 16 whereby no direct physicalcontact can be made with race 15 to, for example, apply a load. Undersome conditions, for example, as shown in FIG. 5, axle nut 11 may besmaller in diameter than inner race 15 where inner race 15 may bedirectly contacted, for example, by housing 142, to provide a load. Inthe aspect of the invention shown in FIGS. 8-11, a specially designedaxle nut 220 having a recess that exposes the surface of inner race 15and permits contact by for example, loading adapter 210. According toaspects of the invention, loading adapter 210 transmits the compressiveload from nut 48 and/or means 244 to inner race 15 of bearing 16, andthus to bearing 18. In one aspect, where race 15 is exposed, loadadapter 210 may be used with a conventional axle nut, for example, axlenut 11 in FIG. 3. However, when inner race 15 would be concealed by aconventional axle nut, modified axle nut 220 may be used according toaspects of the invention.

In contrast to other aspects of the invention, for example, thoseillustrated in FIGS. 4 and 5, the aspect of the invention shown in FIGS.8-11 may provide a more accurate and reproducible indication of anexisting or desired preload on bearings 16 and 18. For example, sincethe load applied, for example, via means 244, is directed to bearing 16and from bearing 16 to bearing 18, the load monitored and indicated bymeans 244 is thus a more accurate indicator of the combined preload onbearings 16 and 18, for instance, no load bearing relationship need beassumed regarding the relative preloads on bearing 16 and 18.

FIG. 12 is perspective view of the bearing loading adapter 210 shown inFIG. 11. FIG. 13 is a side elevation view of the bearing loading adapter210 shown in FIG. 12 and FIG. 14 is top plan view of bearing loadingadapter 210 shown in FIG. 12. As shown, adapter 210 includes a plate 211and at least two extensions, fingers, or arms 212, 213 from plate 211.In this aspect of the invention, extensions 212 and 213 are adapted totransmit the load applied to plate 211, for example, by the compressionof nut 48, to the bearing 16. As shown in FIGS. 12-13, plate 211typically includes a through hole or bore 214 that is adapted to receiverod 40, as shown in FIG. 11. Plate 211 may also include a raised boss215 adapted to contact means 244 for example, adapted to contact piston54 or bearing 64 (see FIG. 4). In one aspect, extensions 212 and 213 maybe moveable or deflectable to facilitate assembly of adapter 210 intoengagement with bearing 16. For example, extensions 212 and 213 mayinclude any interface with plate 211 or modification to extensions 212and 213 that permits extensions 212 and 213 to deflect to avoidinterference with nut 11 or nut 220. As shown in FIGS. 12-14, in oneaspect, extensions 212 and 213 may be pivotally mounted to plate 211.Plate 211 may include a pair of lugs or projections 216 having throughholes 217 and extensions 212, 213 may include recesses 218 adapted toreceive projections 216 and extensions 212, 213 may include throughholes 219. Pins 222 may be provided in holes 219 in extensions 212, 213that engage holes 217 in projections 216 whereby extensions 212, 213 mayrotate about pins 222 as indicated by double arrows 224 in FIG. 13.

Arms or extensions 212, 213 may include projections 225, 226,respectively, for example, arcuate projections adapted to engage thearcuate shape of inner race 15 of bearing 16. Arcuate projections 225,226 may be radiused to provide the same curvature of inner race 15, forexample, a radius of between about 1¼ inches and about 3 inches.Projections 225, 226 may include shoulders 227, 228, respectively, toassist in engaging race 15. In one aspect, since pins 222 (whichtransmit the load from plate 211 to extensions 212, 213) may be locatedat a greater radial distance from the center of shaft 14 than the radialdistance to the point of contact on inner race 15 (see FIG. 11),shoulders 227, 228 may be provided to minimize or prevent contact ofprojections 225, 226 with nut 220. This aspect of the invention mayensure that the compressive load applied by means 244 is transmitted torace 15 and not borne by nut 220. Minimizing or preventing contactbetween extensions 212, 213 and nut 220 also permits nut 220 to befreely rotated without contact with extensions 212, 213.

Although only two extensions 212, 213 are illustrated in FIGS. 12-14,according to one aspect of the invention, two or more extensions 212,213 may be mounted to plate 211. For example, three or more extension212, 213 may be provided, for example, uniformly spaced about plate 211.In one aspect, plate 211 may be a circular plate having two or moreextensions 212, 213. In one aspect of the invention, extensions 212, 213may include spring-loaded mountings to plate 211 whereby extensions 212,213 are biased into a position of engagement with race 215. Adapter 210and its components may be fabricated from any conventional structuralmetal, for example, iron, steel, stainless steel, aluminum, titanium,nickel, magnesium, brass, or bronze, among others.

FIG. 15 is a perspective view of an axle nut 220 according to anotheraspect of the invention. FIG. 16 is a side elevation view, partially incross section, of axle nut 220 shown in FIG. 15. As shown in FIGS. 15and 16, nut 220 includes a cylindrical body 240 having a first end 241and a second end 242 and a longitudinal axis 246. Cylindrical body 240may be a circular cylindrical body or a non-circular cylindrical body,for example, a polygonal cylindrical body, such as body having atriangular, square, pentagonal, hexagonal, or octagonal cross section,among others, having a plurality of flat sections, that is, “flats.”

Second end 242 includes a face 248 adapted to contact the face of innerrace 15 (see FIG. 11). Body 240 includes a threaded through hole or bore250 directed substantially along the longitudinal axis 246 of body 240.The threads of through hole 250 may comprise any conventional UN, UNC,UNF, UNJ, Acme, or other conventional thread. In one aspect, of theinvention where nut 220 is used for a conventional truck axle, threadedthrough hole 250 may have 12 to 18 threads per inch UN threads.

According to aspects of the present invention, second end 242 of body240 may include at least one recess 252 in face 248. As described above,recess 252 in the face 248 exposes at least a portion of the matingsurface against which nut 220 bears whereby a compressive load may beapplied, for example, to apply a compressive load to the face of innerrace 15 of bearing 16 (see FIG. 11). As described above, this exposureof the face of race 15 permits a mechanic to apply and/or verify apreload on bearing 16, for example, to verify a preferred “3thousandths” preload discussed previously.

In the aspect of the invention shown in FIGS. 15 and 16, recess 252 isshown as a single annular or arcuate recess whereby a raised boss 254 isprovided on second end 242. FIG. 20 is a plan view of an axle nut 320having a body 340 and a threaded through hole or bore 350 according toanother aspect of the invention. However, according to one aspect of theinvention, the at least one recess 252 may comprises one or morecavities in surface 248, for example, one or more cavities evenlydistributed about the perimeter of the second end 242. For instance, inone aspect of the invention, as shown in FIG. 20, recess 252 maycomprise a plurality of arcuate cavities or recesses 352 evenlydistributed about the perimeter of second end 342 and adapted to exposethe surface of the mating surface, for example, whereby two or moreextensions on adapter 210, for example, extensions 212, 213 in FIG. 12,may contact the mating surface, for example, the mating surface ofbearing 16. As shown in FIG. 16, the diameter of boss 254, or the insidediameter of the plurality of recesses in second end 242 may have adiameter 255. According to one aspect of the invention, diameter 255 issized to provide sufficient support for inner race 15 while providing atleast some exposure to the surface of race 15 whereby a loading device,for example, adapter 210, may contact inner race 15. For example,diameter 255 may be at least as large as the minimum “backing diameter”recommended by the manufacturer of bearing 16.

As shown in FIGS. 15 and 16, first end 241 of body 240 may be adapted toaccommodate a nut locking mechanism, for example, the nut lockingmechanism disclosed in co-pending and commonly-assigned application Ser.No. 11/029,531 entitled “Lock Nut System” filed on Jan. 5, 2005, thedisclosure of which is included by reference herein. For example, firstend 241 of body 240 may include a counter bore 256 having a plurality ofinternal projections 258 and an annular groove 260. Internal projections258 may be gear teeth or spline teeth adapted to engage a locking device(not shown) and annular groove 260 may be adapted to retain a lockingdevice retainer (not shown), such as described in co-pending applicationSer. No. 11/029,531. In one aspect of the invention, no counter bore 256or annular groove 260 may be provided in first end 241 whereby first end241 may only comprise a flat surface interrupted by threaded throughhole 250.

Body 240 may also be adapted to be engagable by a tool, for example, acrescent wrench, spanner wrench, or socket, among other tools, wherebybody 240 may be rotated as desired. In one aspect, as shown in FIGS. 15and 16 body 240 may comprise an outside surface 262 having at least oneflat 264, but typically a plurality of flats 264 adapted to engage atool, such as a wrench or socket. In another aspect body 240 may includeat least one recess, hole, or slot adapted to engage a spanner-typetool. For example, in one aspect, as shown in FIG. 20, outside surface362 of body 340 may include holes or slots 364 (shown in phantom)adapted to engage a spanner wrench. In another aspect of the invention,any other surface of body 240, 340 may include recesses, holes, or slotsadapted to engage a spanner-type wrench, for example, the surface of end241 may include a plurality of equally spaced holes or the surface ofcounter bore 256 may include a plurality of equally spaced holes. Otheradaptations of body 240, 340 to facilitate engagement by a tool forrotating nut 220, 320 will be apparent to those of skill in the art.

Nut or fastener 220 may be fabricated from any one or more thestructural metals mentioned above, for example, carbon steel orstainless steel. Nut 220 may be fabricated by machining from a billet orplate, by forging or casting and then finished machining, or fabricatedby conventional powder metallurgy techniques. In one aspect, when formedby powder metallurgy, the material may be FC 0208, or its equivalent.Nut 220 may also be surface hardened for example, induction hardened,carburized, or nitrided, among other surface hardening methods; in oneaspect, the exposed surfaces on end 241 of nut 220 may be hardened, forexample, induction hardened.

One method of providing a preload to an axle bearing and minimizing thelikelihood of losing the preload is to provide a nut arrangementincluding a first load adjusting nut, a lock washer that prevents theload adjusting nut from loosening, and a second jam nut that bearsagainst the lock washer to secure the lock washer in place. Such ahardware arrangement can be found in most conventional originalequipment truck and trailer axles. However, in this prior artarrangement, the first load adjusting nut is typically at least as largein diameter as the inner race of the bearing to which it applied.Therefore, when employing such prior art nut arrangements, the innerrace is typically not accessible by a bearing loading or verificationdevice, such as aspects of the invention. However, the aspect of theinvention shown in FIGS. 17-19 addresses the limitations of the priorart bearing loading devices by, among other things, allowing access tothe inner bearing race for loading and/or preload verification when anut-lock washer-jam nut arrangement is provided.

FIG. 17 illustrates still another aspect of the invention for applyingor verifying a load or preload to a bearing. FIG. 17 is a sideelevational view, partially in cross section, of an apparatus 300 forapplying or verifying a load or preload on a bearing according toanother aspect of the invention. FIG. 17 is a view similar to FIG. 11and includes many of the structures that may have similar if notidentical functions to those structures that appear in FIG. 11. Thesesimilar structures are identified in FIG. 17 by the same referencenumbers shown in FIG. 11. Some of these common structures shown in FIG.17 include wheel hub 12, shaft 14 (shown in cross section in FIG. 17),inner bearing 16 having inner race 15, and means 244 having shaft 40,coupling 46, nut 48, gage 60, and adapter 210. According to this aspectof the invention, apparatus 300 also includes a nut or fastenerarrangement 270 that is an alternative to nut 220 shown in FIG. 11. Nutarrangement 270 includes a first internally threaded ring 272, a secondring 274, and a third threaded ring 276. According to this aspect of theinvention, nut arrangement 270 provides a means for ensuring a preloadis maintained in bearing 16 while minimizing or preventing the removalof this preload, for example, during normal operation of the vehicle. Inaddition, arrangement 270 also provides access to inner race 15 wherebya bearing loading device, such as adapter 210, may access the surface ofinner race 15 to provide a desired load or preload to the inner race 15.For example, close examination of FIG. 17 with nut arrangement 270installed, illustrates how a surface of inner race 15 can be contactedby extensions 212 of adapter 210.

FIG. 18 is a perspective view, partially in cross section, of nutarrangement 270 shown in FIG. 17. FIG. 19 is an exploded perspectiveview of the elements of nut arrangement 270 shown in FIGS. 17 and 18. Asshown in FIGS. 18 and 19, nut arrangement 270 includes a first threadedring or nut 272, a second ring 274, and a third threaded ring or nut276. As noted with respect to diameter 255 of nut 220 in FIG. 16, theouter diameter of ring or nut 272 may have a diameter sized to providesufficient support for inner race 15 while providing at least someexposure to the surface of race 15 whereby a loading device, forexample, adapter 210, may contact inner race 15. For example, the outerdiameter of ring or nut 272 may be at least as large as the minimum“backing diameter” recommended by the manufacturer of bearing 16.

Ring or nut 272 includes internal threads 273 adapted to threadablymount to shaft 14 and engage the inner bearing race 15 (see FIG. 17).Ring or nut 272 includes an outer surface 278 that may be engagable by atool, for example, a crescent wrench, spanner wrench, or similar tool.For example, as shown in FIGS. 18 and 19, the outer surface 278 of ringor nut 272 may include one or more grooves 279 engagable by aspanner-type wrench. Grooves 279 may also be slots, notches, holes, orother indentations in surface 278. In lieu of or in addition to grooves279, the outer surface 278 of ring 272 may include projections, forexample, one or more spokes, engagable by a tool or a mechanic. Also,according to an aspect of the invention, ring or nut 272 may have anouter diameter that is less than the outer diameter of inner race 15,that is, whereby at least a portion of the longitudinal surface of race15 is accessible for contact by, for example, adapter 210 (again, seeFIG. 17). Ring or nut 272 may also include means for engaging ring 274to prohibit relative movement, specifically relative rotationalmovement, between ring 272 and ring 274. For example, as shown in FIGS.18 and 19, ring 272 may include one or more projections or pins 280adapted to engage a hole or a recess in ring 274. Pin 280 may be pressor shrink fit into ring 272 or pin 280 may simply be punched into ring272. In one aspect of the invention, ring 272 may include a hole or arecess that accepts a projection or pin in ring 274. Threads 273 may beany one of the threads mentioned above, but are typically 12 to 18threads per inch UN threads.

Second ring 274 is also adapted to mount to shaft 14 (see FIG. 17) andincludes means for engaging ring 272 to prohibit relative movementbetween second ring 274 and first ring 272 and second ring 274 includesmeans for engaging shaft 14 to prohibit relative movement between secondring 274 and shaft 14, specifically prohibit rotational movement. Forexample, as shown in FIGS. 18 and 19, ring 274 may include one or moreholes or recesses, for example, through holes 282. Through holes 282 areadapted to engage one or more pins or protections 280 in ring 272 toprohibit relative rotational movement between ring 274 and ring 272.Again, in one aspect, ring 274 may include one or more pins orprojections, similar to pin 280, that are adapted to engage one or moreholes or recesses in ring 272. The means for engaging shaft 14 in ring274 may comprise any recess or projection adapted to engage shaft 14.For example, as shown in FIGS. 18 and 19, ring 274 may include one ormore projections or key-type structures adapted to engage a recess inshaft 14. For example, ring 274 may include one or more key-typeprojections 284 that are adapted to engage a slot or keyway 285 in shaft14 (see FIG. 17). In one aspect, arrangement 270 may include one or moreseparate individual keys that are adapted to engage one or more keywaysin ring 274 and one or more keyways 285 in shaft 14.

Third threaded ring or nut 276 includes internal threads 277 adapted tothreadably mount to shaft 14 and engage second ring 274 (see FIG. 17).Ring or nut 276 includes an outer surface 286 that may, similar to ring272, be engagable by a tool, for example, a crescent wrench, spannerwrench, or similar tool. For example, as shown in FIGS. 18 and 19, theouter surface 286 of ring or nut 276 may include one or more flats 287engagable by a crescent-type wrench. In one aspect outer surface 286 mayalso include grooves, slots, notches, holes, or other indentationsadaptable to be engaged by a spanner-type wrench. Threads 277 may be anyone of the threads mentioned above, but are typically 12 to 18 threadsper inch UN threads.

Ring 272, ring 274, and ring 276 may be fabricated from any one or morethe structural metals mentioned above, for example, carbon steel orstainless steel. Ring 272, ring 274, and ring 276 may be fabricated bymachining from a billet or plate, by forging or casting and thenfinished machining, or fabricated by conventional powder metallurgytechniques. In one aspect, when formed by powder metallurgy, thematerial may be FC 0208, or its equivalent. Ring 272, ring 274, and ring276 may also be surface hardened for example, induction hardened,carburized, or nitrided, among other surface hardening methods.

As shown in FIG. 17, according to one aspect of the invention, nutarrangement 270 may be used to secure bearing 16 to shaft 14 while alsoproviding access to the surface of inner race 15 of bearing 16 whereby abearing loading device may contact inner race 15. In one aspect, duringa new installation or during servicing of an existing bearing,arrangement 270 permits access to inner race 15 by, for example, loadingadapter 210. In an original installation, after bearing 16 is mounted toshaft 14 and hub 12, ring 272 may be threaded to shaft 14 and tightened,for example, hand tightened, against the exposed longitudinal surface ofinner race 15. The bearing loading apparatus 244 may then be mounted toshaft 14 as described above, for example, where rod 40 is engaged withshaft 14 by means of collar 46, adapter 210 is mounted to rod 40 andinner race 15, and housing 52 (having piston 54) and nut 48 are mountedto rod 40. Then, according to aspects of the invention, a load may beapplied to inner race 15, for example, mechanically by turning nut 48and/or hydraulically by introducing a pressurized fluid to housing 52.The loading on inner race 15 may be monitored, for example, by means ofpressure gauge 60, until the desired loading on inner race 15 isprovided. After a load is applied to race 15, the hub assembly 12 may berotated about shaft 14 to ensure proper seating of the rollers ofbearing 16. This rotation and seating may be practiced repeatedly toensure proper seating. According to aspects of the invention, with thedesired loading on inner race 15 provided, ring or nut 272 may betightened, for example, by using a spanner wrench engaging grooves 279,to maintain the desired loading on inner race 15.

In one aspect, the rollers in bearings 16 and 18 may be properly seatedby applying a roller-seating load to the inner race 15, that is, a loadsufficient to seat the rollers in bearings 16 and 18. For example, aroller-seating load may correspond to a hydraulic pressure in housing 52of between about 900 psig and about 1000 psig, as detected by gauge 60.(In one aspect, this hydraulic pressure may correspond to a bearing loadof between about 5000 pounds to about 6000 pounds, for example, ascomputed by Equation 1.) Again, hub 12 may be rotated one or more timeswhile this seating load is applied to ensure proper seating of all therollers. After proper seating of the rollers, the applied load may bereduced to a load corresponding to the desired preload on the bearings,for example, a load providing a few thousands inches preload. Thisdesired preloading may be provided by between about 50 psig and 100 psighydraulic pressure in housing 52 of means 244. (In one aspect, thishydraulic pressure may correspond to a bearing load of between about 300pounds to about 600 pounds, for example, as computed by Equation 1.)Once the desired preload is provided, ring or nut 272 may be tightened,for example, by hand or with a tool, to maintain the desired preload.

Apparatus 244 is then removed, and ring 274 can be mounted to shaft 14whereby at least one through hole 282 engages one or more pins 280 onring 272 and key 284 engages keyway 285 in shaft 14. These interferencesof ring 274 with ring 272 and shaft 14 substantially prohibit relativerotational motion between ring 272 and shaft 14 whereby the preload oninner race 15 is substantially maintained. Then, ring or jam nut 276 isthreaded onto shaft 14 and tightened against ring 274 to secure ring 274to shaft 14. Other procedures and procedural modifications of thismethod will be apparent to those of skill in the art.

In another aspect, the preloading on a bearing of an existing hubassembly may be verified or evaluated with the wheel in place orremoved. In this aspect of the invention, nut arrangement 270 may bemounted to shaft 14 whereby a preload may or may not be present on innerrace 15 of bearing 16. Third ring 276 and second ring 274 may be removedto obtain access to ring 272 whereby ring 272 may be rotated about shaft14, if necessary. In one aspect, where sufficient play between hardwareis provided, third ring 276 and second ring 274 need not be removed.Also, when a nut such as nut 220 in FIG. 11 is provided with a lockingmechanism (for example, the locking mechanism disclosed in pending U.S.application Ser. No. 11/029,531), the locking mechanism need not beremoved when sufficient play is available between hardware to detectloosening of the nut.

Apparatus 244 having rod 40, adapter 210, housing 52, and nut 48 maythen be mounted whereby adapter 210 engages inner race 15. According toaspects of the invention, inner race 15 may be contacted by adapter 210since the outer diameter of ring 272 is less than the outer diameter ofinner race 15. The loading on inner race 15 is then gradually increased,either mechanically or hydraulically. At the same time or alternatingwith the increase in load, the tightness of ring 272 against inner race15 may be checked, for example, manually, to determine when the preloadon inner race 15 is relieved by the applied load via adapter 210. If nutor ring 272 becomes loose prior to achieving the desired preload for thespecific bearing, the preload can be increased to the desired value, forexample, as indicted by gauge 60, and then ring 272 tightened tomaintain the desired preload. If the preload on inner race 15 issatisfactory, that is, nut or ring 272 does not loosen until about thedesired preload is achieved, nut or ring 272 can be tightened tomaintain the desired preload. Should the actual preload exceed thedesired preload, the load applied by apparatus 244 can be increaseduntil ring or nut 272 becomes loose, and then the load reduced to thedesired preload, and nut or ring 272 retightened to maintain the desiredpreload. Apparatus 244 may then be removed and rings 274 and 276remounted according to the invention to ensure the desired preload isprovided.

Again, the inventor underscores that though aspects of the presentinvention were described above with respect to their application towheel hub assemblies, for example, truck wheel hub assemblies, it isunderstood that aspects of the present invention may be applied to anyvehicle, machine, or component having at least one bearing.

While several aspects of the present invention have been described anddepicted herein, alternative aspects may be effected by those skilled inthe art to accomplish the same objectives. Accordingly, it is intendedby the appended claims to cover all such alternative aspects as fallwithin the true spirit and scope of the invention.

The invention claimed is:
 1. An axle nut comprising; a cylindrical body having a first end comprising a circumferential slot receiving a retaining member; said cylindrical body having a plurality of engaging teeth; said retaining member secured to a keeper; said keeper having a plurality of keeper teeth engaging said plurality of engaging teeth to inhibit movement of said keeper relative to said body; said keeper having a radially inner side configured to engage a shaft to inhibit rotational movement of said body relative to the shaft; said retaining member engageable with said nut to hold said keeper axially such that said plurality of keeper teeth are engaged with said plurality of engaging teeth; said retaining member is formed of a material different than said keeper such that said retaining member is more flexible than said keeper; and a longitudinal axis, an outer surface engagable by a tool to rotate the axle nut, and a second end having means for bearing against a surface, the means for bearing against the surface comprising a face; a helically threaded through-hole directed substantially along the longitudinal axis of the cylindrical body of the axle nut to threadably engage an axle; and means for accessing an inner race of a bearing at the face of the second end of the body by an apparatus for applying a load to the bearing.
 2. The nut as recited in claim 1, wherein the means for accessing comprises at least one recess.
 3. The nut as recited in claim 2, wherein the at least one recess comprises a plurality of arcuate recesses equally spaced about the perimeter of the face.
 4. The nut as recited in claim 2, wherein the at least one recess comprises a single annular recess extending around the perimeter of the face of the second end.
 5. The nut as recited in claim 1 wherein the retaining member extends continuously in an arc from a first outside end to a second outside end, said keeper located between said first end and said second end.
 6. The nut as recited in claim 1, wherein the nut comprises a bearing retaining nut and the surface comprises a surface of a bearing.
 7. The nut as recited in claim 6, wherein the at least one recess is adapted to expose at least a portion of the surface of the bearing whereby a compressive load can be applied to the surface of the bearing.
 8. The nut as recited in claim 2, wherein the at least one recess in the face of the second end comprises at least one cavity in the face of the second end.
 9. The nut as recited in claim 8, wherein the at least one cavity comprises a plurality of evenly distributed cavities.
 10. The nut as recited in claim 1, wherein the outer surface engagable by a tool comprises an outer surface engagable by one or more of a crescent wrench, a spanner wrench, and a socket.
 11. The nut as recited in claim 1, wherein the nut is fabricated by powder metallurgy.
 12. The nut as recited in claim 1, wherein the nut includes at least one surface that is surface hardened.
 13. The nut as recited in claim 1, wherein the face comprises a surface.
 14. An axle nut system comprising; a cylindrical body having a first end, a longitudinal axis, an outer surface engagable by a tool to rotate the axle nut, and a second end having means for bearing against a surface, the means for bearing against the surface comprising a face; said body having a plurality of engaging teeth; a keeper having a plurality of keeper teeth engageable with said plurality of engaging teeth to inhibit movement of said keeper relative to said body when said plurality of engaging teeth engages said plurality of keeper teeth; said keeper having a radially inner side configured to engage a shaft to inhibit rotational movement of said body relative to the shaft when said plurality of engaging teeth engages said plurality of keeper teeth and said radially inner side engages the shaft; a separate keeper retaining member secured to said keeper, said retaining member engageable with said nut to hold said keeper axially such that said plurality of keeper teeth are engaged with said plurality of engaging teeth, said retaining member extending continuously in an arc from a first outside end to a second outside end, said keeper located between said first end and said second end; and a helically threaded through-hole directed substantially along the longitudinal axis of the cylindrical body of the axle nut to threadably engage an axle.
 15. An axle nut system comprising; a cylindrical body having a first end, a longitudinal axis, an outer surface engagable by a tool to rotate the axle nut, and a second end having means for bearing against a surface, the means for bearing against the surface comprising a face; said body having a plurality of engaging teeth; a keeper having a plurality of keeper teeth engageable with said plurality of engaging teeth to inhibit movement of said keeper relative to said body when said plurality of engaging teeth engages said plurality of keeper teeth; said keeper having a radially inner side configured to engage a shaft to inhibit rotational movement of said body relative to the shaft when said plurality of engaging teeth engages said plurality of keeper teeth and said radially inner side engages the shaft; and a keeper retaining member connected to said keeper and engageable with said body to hold said keeper axially such that said plurality of keeper teeth are engaged with said plurality of engaging teeth, said retaining member being formed of a material different than said keeper such that said retaining member is more flexible than said keeper; and a helically threaded through-hole directed substantially along the longitudinal axis of the cylindrical body of the axle nut to threadably engage an axle.
 16. A lock nut system comprising: a nut having a plurality of engaging teeth; said nut having a cylindrical body and a helically threaded through-hole directed substantially along the longitudinal axis of the cylindrical body to threadably engage an axle; a keeper having a plurality of keeper teeth engageable with said plurality of engaging teeth of said nut to inhibit movement of said keeper relative to said nut when said plurality of engaging teeth engages said plurality of keeper teeth; said keeper having a radially inner side configured to engage a shaft to inhibit rotational movement of said nut relative to the shaft when said plurality of engaging teeth engages said plurality of keeper teeth and said radially inner side engages the shaft; a keeper retaining member secured to said keeper, said retaining member engageable with said nut to hold said keeper axially such that said plurality of keeper teeth are engaged with said plurality of engaging teeth; and at least one recess in a face of said nut, the at least one recess configured to expose at least a portion of a surface said nut bears against.
 17. The system of claim 16, wherein said at least one recess comprises at least one arcuate recess.
 18. The system of claim 16, wherein said at least one arcuate recess comprises a plurality of arcuate recesses equally spaced about the perimeter of a face of said nut.
 19. The system of claim 16, wherein said at least one recess is bounded by a curved outer surface of said nut extending around a perimeter of said nut.
 20. The system of claim 16, wherein said inner side of said keeper comprises a shaft engaging member engageable in a shaft slot of the shaft to inhibit rotational movement of said nut relative to the shaft.
 21. The system of claim 16, wherein said nut further comprises a nut slot for receiving said keeper retaining member.
 22. The system of claim 21, wherein said keeper retaining member comprises at least one leg configured to be received in said nut slot.
 23. The system of claim 22 wherein said keeper retaining member is configured to hold said keeper axially relative to said nut such that said plurality of engaging teeth and said plurality of keeper teeth are engaged when said at least one leg is received in said nut slot.
 24. The system of claim 23, wherein said at least one leg comprises two legs elastically deformable toward one another to allow said retaining member to be attached to said nut by inserting said two legs in said nut slot.
 25. The system of claim 16, wherein said retaining member is formed of a material different than said keeper, such that said retaining member is more flexible than said keeper.
 26. The system of claim 16, wherein said retaining member extends continuously in an arc from a first outside end to a second outside end, said keeper located between said first end and said second end. 